WO2010040511A1 - Ensemble soupape de limitation de pression et soupape anticavitation - Google Patents

Ensemble soupape de limitation de pression et soupape anticavitation Download PDF

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Publication number
WO2010040511A1
WO2010040511A1 PCT/EP2009/007189 EP2009007189W WO2010040511A1 WO 2010040511 A1 WO2010040511 A1 WO 2010040511A1 EP 2009007189 W EP2009007189 W EP 2009007189W WO 2010040511 A1 WO2010040511 A1 WO 2010040511A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
closing body
seat
pin
Prior art date
Application number
PCT/EP2009/007189
Other languages
German (de)
English (en)
Inventor
Markus GEPRÄGS
Erik Wilhelm
Stefan Joksch
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to CN2009801396499A priority Critical patent/CN102177375B/zh
Priority to US13/122,473 priority patent/US20110240897A1/en
Publication of WO2010040511A1 publication Critical patent/WO2010040511A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/18—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on either side
    • F16K17/19—Equalising valves predominantly for tanks
    • F16K17/196—Equalising valves predominantly for tanks spring-loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/024—Pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/044—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with more than one spring

Definitions

  • the invention relates to a pressure limiting and Nachsaugventiliser.
  • German Offenlegungsschrift DE 10 2004 061 862 A1 discloses a pressure limiting and evacuation valve unit with a pressure limiting function according to the preamble of claim 1.
  • the valve unit comprises a valve closing body having a valve closing surface which forms a first sealing seat for the feed function together with a valve closing surface opposite the first valve seat, and which has a valve closing body opening, which is surrounded by a second valve seat, which together with a at a formed axially movable valve pin closing head forms a second sealing seat for the pressure limiting function.
  • a spring plate, the valve closing body and the valve pin are guided in different bore sections.
  • German published patent application DE 10 2004 061 862 A1 it has already been proposed in German published patent application DE 10 2004 061 862 A1, to achieve a pressure equalization between a first pressure region and a blind bore into which only the valve pin extends in sections through a longitudinal bore over the entire length of the valve pin.
  • the force exerted in the opening direction on the valve closing body only by a Differential area determined from the blind bore cross section and the valve closing surface. It can be realized by small difference surfaces small opening forces and thus springs with low spring constants.
  • a disadvantage of the known pressure limiting and Nachsaugventiltician is that the leadership of the valve pin from the valve closing body opening into the blind bore leads to a very long valve pin and an overdetermined system. This results in short lifetimes of the pressure relief and suction valve unit and high, unpredictable, in-service friction effects that can adversely affect the opening characteristics of the pressure relief and suction valve unit.
  • the long valve pin leads in addition to an overall very long pressure relief and Nachsaugventiltician for the large installation spaces must be provided, which are expensive or partially not available.
  • the space provided for the arrangement of the springs is relatively small.
  • the invention has for its object to provide a comparison with the prior art improved pressure limiting and suction valve.
  • a slight adaptation of the opening cross-section for the pressure limiting function and the pressure-effective surface to be realized and the long-term function of the valve unit can be ensured.
  • the pressure limiting and suction valve unit has a first sealing seat and a second sealing seat.
  • the first and second sealing seats each separate a first pressure area from a second pressure area.
  • the first sealing seat is through Cooperation of a valve closing body on which a first valve closing surface is formed, formed with a first valve seat.
  • the second sealing seat is formed between the valve closing body and a valve pin.
  • a closing head On the valve pin, which is axially movable, a closing head is formed, which cooperates sealingly to form the second sealing seat with a valve seat opening surrounding a second valve seat.
  • a first closing spring is provided, which is arranged between the valve closing body and a spring plate. The spring plate is for this purpose connected to the valve pin.
  • a second closing spring biases a valve assembly against the first valve seat.
  • the valve assembly includes the valve pin, the valve closing body and the components required for biasing the valve pin against the valve closing body, namely first closing spring and spring plate.
  • the valve pin is now guided in the valve closing body.
  • at least one first guide section is formed in the valve closing body, in which the valve pin is guided sealed in a longitudinally displaceable manner.
  • the seal is preferably carried out by a correspondingly close tolerance of the diameter of the valve pin and the guide portion.
  • This first guide portion is formed with respect to the direction of movement of the valve pin on the side facing away from the second sealing seat side of the valve closing body.
  • the first guide section separates a volume connected to the first pressure area from the second pressure area or from a volume connected to the second pressure area. Further, a cross-sectional area of the first guide portion is smaller than a cross-sectional area of the second valve seat.
  • the size of one with the Adjust the pressure of the second pressure area to the applied surface of the valve pin By means of this procedure for adjusting the area of the valve pin which is acted upon by the pressure of the second pressure region, an adaptation to the spring force which is required for closing against the pressure of the second pressure region can be carried out in a simple manner.
  • the hydraulic opening force can be adapted, for example, after changing an outflow cross section of the second sealing seat by adapting the cross-sectional area in the first guide section.
  • valve closing body a volume which is connected to the first pressure region or the second pressure region and which is arranged such that a radial step formed on the valve pin is arranged within the axial extent of the volume and prevailing there Pressure is applied.
  • the pressure-effective area is adjustable in particular independently of the diameter of the second valve seat.
  • a change in the diameter of the valve seat can be compensated by appropriate adjustment of the radial stage. In this way, it is possible in each case to produce an effective surface, which can be acted upon by the pressure of the second pressure region, on the valve bolt, which matches a specific, selected closing spring. The re-tuning after adjusting the outflow cross section at the second sealing seat by selecting suitable closing springs can thus be dispensed with.
  • the connecting channel is preferably guided in the valve closing body.
  • a spring chamber is preferably formed, in which the first and the second closing spring are arranged.
  • This spring chamber is preferably connected to the respective other pressure range.
  • the first guide section thus preferably separates a volume, which is formed within the valve closing body, from a volume of the spring chamber, wherein one of the two regions is connected to the first pressure region and the respective other volume is connected to the second pressure region.
  • valve closing body In order to be able to act on the end face of the valve pin facing away from the closing body with the pressure of the second pressure region, it is particularly advantageous if the valve closing body is guided with a clearance fit in a receiving recess, which simultaneously forms the spring chamber.
  • the spring chamber is thus connected to the second pressure range via the clearance between the valve closing body and the housing part or via an extra trained connecting channel.
  • a clearance fit means that an outer diameter of the valve closing body is always made slightly smaller than the diameter of the valve closing body receiving bore.
  • a further simplification in production results when the diameter of the first sealing seat and the guide diameter of the valve closing body are equal. In this way, the number of required drilling tools is reduced.
  • FIG. 2 is a sectional view of a second embodiment of a pressure limiting and Nachsaugventiliser invention with a radial step on the valve pin.
  • FIG. 1 shows an exemplary embodiment of the pressure limiting and suction valve unit 1 according to the invention. DESCRIPTION OF THE PREFERRED EMBODIMENT Before describing the structure and function of the pressure limiting and suction valve unit 1, an application example of the pressure limiting and suction valve unit 1 according to the invention will be described to clarify the function.
  • Pressure limiting and suction valve units 1 find z. As in closed hydraulic circuits an important application. Since hydrostatic machines always lose some liquid due to leakage, the liquid quantity must be compensated by supplying pressure fluid, in order to keep constant the pressure medium quantity in the working lines, which connect hydraulic motor and pump. Therefore, Nachsaugventile feed from a feed system in which a low pressure of, for example, about 25 bar, required amounts of pressure medium in a working line, if a pressure drop in the working line below a set or constructive limit for an opening pressure of the Nachsaugventils the pressure limiting and Nachsaugventiltechnik in a first direction of the pressure gradient takes place.
  • Infeed of pressure medium is a pressure medium source, usually in the form of a feed pump provided.
  • Valve body part 3 is screwed in and by means of a
  • Valve housing part 3 are a feed terminal 5 z. B. the above-described feed system as the first pressure range and a working line connection 6 as the second
  • Suction valve unit 1 can be connected to each other.
  • valve closing body 7 At its the feed terminal 5, which is connected in the example described above with the feed system, not shown, facing the end, the Druckbegrenzungs- and Suction valve unit 1 on a valve closing body 7, on which an approximately frusto-conical in the embodiment formed valve closing surface 8 is formed.
  • the valve closing surface 8 cooperates with a valve seat 8 opposite the first valve seat 9 to form a first sealing seat.
  • the first valve seat 9 is formed in the second valve housing part 3.
  • the valve closing body 7 also has a valve closing body opening 11, which is surrounded on its circumference by a second valve seat 12.
  • the second valve seat 12 cooperates with a provided on a valve pin 13 closing head 14 to form a second sealing seat.
  • the valve pin 13 extends through the valve-closing body opening 11 therethrough.
  • the valve pin 13 is connected to a spring plate 15.
  • a first closing spring 10 extends between the spring plate 15 and the valve closing body 7 so that the first closing spring 10 is clamped between the spring plate 15 and the valve closing body 7.
  • the closing head 14 of the valve pin 13 is held in sealing engagement with the valve seat opening 11 surrounding the second valve seat 12.
  • the valve pin 13, the first closing spring 10, the spring plate 15 and the part of the valve closing body 7 facing away from the valve closing head 13 are received in the first valve housing part 2 by an axial bore as a receiving recess 16.
  • the spring plate 15 is secured by a securing body 17, such as a lock nut, on the valve pin 13.
  • a securing body 17 such as a lock nut
  • the valve pin 13 is provided at the end facing away from the closing head 14 with an external thread 23, which with a corresponding internal thread of the spring plate 15 and the fuse body 17, which counteracts the spring plate 15, acts together.
  • the axial position of the spring plate 15 relative to the valve pin 13 is therefore variable by rotating the valve pin 13 relative to the spring plate 15, whereby the bias of the first closing spring 10 is adjustable.
  • valve pin 13 is no longer guided in an additional blind bore at the base of the axial bore.
  • the longitudinal bore 53 of the valve pin 13 opens directly into the spring chamber 18 of the first housing part 2 and thus connects the first pressure region 5 with the spring chamber 18.
  • the valve closing body 7 is partially mitaufêt in the receiving recess 16 and there with a Guide diameter D guided axially displaceable.
  • the valve closing body 7 is in the Receiving recess 16 guided sealingly with close clearance and there is no fluidic connection between the second pressure region 6 and the spring chamber 18 except for unavoidable leakage flows.
  • valve pin 13 in the valve closing body 7 with a tight play in a guide portion 19 with the diameter di sealingly out to avoid a fluid connection here as well.
  • sealing points and sealing rings may be provided. However, this means extra effort and deteriorates the dynamic behavior of the valve.
  • the valve closing body 7 has a region with a plurality of transverse bores 20, which intersect in the region of symmetry in the region 27 and which penetrate the valve closing body 7 between the first guide section 19 and the second sealing seat.
  • the region 27 and the transverse bores 20 thus likewise belong to the second pressure region, which thus forms a volume separated from the spring chamber 18 via the guide section 19. This volume is permanently at the same pressure level as the working line connection 6.
  • the region 27 is in turn connected to the valve closing body opening 11, so that when lifting the closing head 14 a connection between the feed terminal 5 and the working line connection 6 is made.
  • Suction valve unit During operation of a hydraulic system such as a traction drive two operating conditions can occur in principle: Located in the working line, which is connected to the working line connection 6, high pressure, the prevailing pressure is higher than the pressure prevailing at the feed port 5, the like already described may be 25 bar. In this case, must by the pressure limiting and
  • a hydraulic force acts in the same direction on the valve pin 13 and is caused by the pressure of the first pressure region. This also acts on a differential surface, which results from the different diameters in the region of the guide portion 19 and the second sealing seat 12. If the hydraulic force difference on the valve pin 13 now exceeds the force difference defined by the two closing springs 10, 35, then the closing head 14 lifts off from the second valve seat 12 and connects the first and the second pressure region. Pressure medium can thus from the second pressure range in the first pressure range flow out. By adapting the different diameters in the region of the guide section 19 and the second valve seat 12, an adjustable pressure-effective surface is thus created. The choice of compared to the valve seat 12 reduced diameter di of the guide portion 19 thus allows easy adjustment in terms of the expected pressures.
  • the spring chamber 18 is not realized in the first valve housing part 2 as a longitudinal bore as in the pressure limiting and Nachsaugventiliser 1 of Fig. 1.
  • the spring chamber 18 has rather into which the valve assembly 7 ⁇ 10, 13 ⁇ 15 leading areas in each case a narrowing of the diameter of the receiving recess 16 ⁇ .
  • a first constriction 29 results in the spring plate 15 with play, and a second constriction 30 performs the sealing part of the closure 7 ⁇ , the ⁇ 16 is located in the receiving recess and the spring chamber 18 of the second pressure region separates.
  • Such a receiving recess 16 * z. B. be realized by the casting of the first valve housing part 2 and subsequent machining.
  • the second constriction 30 is radially slightly further than the first constriction 29 in order to be able to easily insert the valve assembly 7, 10, 13, 15 into the receiving recess 16 during production.
  • the working line connection 6 is furthermore connected to the valve closing body opening 11 via the region 27 and the transverse bores 20, which are only partially recognizable due to the position of the section in FIG. A in the valve closure member 7 ⁇ trained connecting channel 25 connects the working line connection 6 having disposed 7 ⁇ in the valve closing body, the valve bolt surrounding 13 ⁇ annular groove 26, which is a connected to the second pressure range volume. In this region of the annular groove 26 is through a step 28 a step-shaped reduction of the diameter of the valve pin 13 ⁇ in the direction of the receiving recess 16 ⁇ realized.
  • l ⁇ is acted upon by the first guide portion 19 of the associated via the longitudinal bore 53 with the first pressure range the spring chamber 18 and connected to the first pressure range by volume from the pressure of the working line Volume or the second pressure range separated. While in the case of the first embodiment of the first guide portion 19 separates the spring chamber 18 from the region 27, in the case of the second embodiment of FIG. 2 in the valve closing body 7 ⁇ the annular groove 26 is provided as connected to the second pressure region volume.
  • valve piston 13 ⁇ can of a diameter d 2 of the second guide portion 21 and thus of the valve piston 13 ⁇ are selected so in the direction of the closing head 14 to be adjacent to the step 28 the second guide portion 21 in the region that it is equal to the diameter of the second sealing seat 12th In the area 27 then act due to the pressure of the second pressure range on the valve piston 13 ⁇ no axial forces.
  • the valve piston 13 ⁇ acting in the opening direction of the relief valve hydraulic forces due to the pressure in the second pressure region act to produce a resultant force exclusively on the step 28 while they cancel each other in the rest.
  • the spring plate 15 and the valve closing body 7 * each have the first closing spring 10 directed towards the valve pin 13 'surrounding shafts, which are designed so that they can center the first closing spring 10 at the ends. This also facilitates the production of the valve assembly 7 ⁇ , 10, 17, 13 x , 15.
  • Fig. 3 shows a third, particularly preferred embodiment.
  • a first guide portion 19 and a second guide portion 21 is also formed between the region 27 and the spring chamber 18 in the valve closing body ⁇ ⁇ 7.
  • the cross-sectional area or the diameter di of the first guide section 19 is again smaller than the cross-sectional area or the diameter d 2 of the second guide section 21.
  • a volume is again provided in the valve body 7 ⁇ ⁇ by an annular channel 26 ⁇ trained.
  • the valve pin 13 ⁇ ⁇ is sealingly but guided in the longitudinal direction displaceable both in the first guide portion 19 and in the second guide portion 21.
  • the step 28 is formed on the valve pin 13 ⁇ ⁇ turn the step 28 is formed.
  • the position of the step 28 and a transverse bore 22 connected to the first pressure region is selected so that both in the closed state of the pressure limiting valve and in the open state due to the axial extent of the annular channel 26 * a fluidic connection of the first pressure region with the volume before Level 28 exists.
  • the annular surface, which is formed by the step 28 each acted upon by the pressure prevailing in the first pressure region.
  • the annular channel 26 ⁇ also creates an advantageous distance between the two guide portions 19 and 21.
  • there is also an advantage for the production since a difficult processing is omitted directly on the diameter jump between the two guide sections.
  • the second guide portion 21 must cooperate sealingly with the valve pin 13 ⁇ ⁇ .
  • a shortened longitudinal bore 53 ⁇ is provided in the valve pin 13 ⁇ '.
  • the shortened longitudinal bore 53 ⁇ opens into the transverse bore 22, so that the annular channel 26 'forms a volume connected to the first pressure region.
  • the transverse bore 22 preferably penetrates the valve pin 13 ⁇ ⁇ along the diameter.
  • the second diameter d 2 corresponds to the diameter of the second guide section 21.
  • the spring chamber 18 is connected via a connecting channel 31 to the second pressure region at the working line connection 6.
  • the connecting channel 31 is formed on the outer periphery of the valve closing body 7 ⁇ ⁇ in the guide region.
  • this is merely to illustrate the connection between the second pressure region and the spring chamber 18.
  • “Clearance” generally means that the outer diameter of the inserted component is smaller than the inner diameter of the female component. Thereby, a gap between the valve closing body l yx and the receiving recess 16 is generated, which allows a pressure equalization between the spring chamber 18 and the second pressure range.
  • the diameter of the second valve seat 12 is the same size as the diameter d 2 of the second guide portion 21.
  • the pressure of the second pressure range effective only one end face 32 of the valve pin 13 ⁇ ⁇ acted upon, whose size by the diameter di given is.
  • the end face 32 of the valve pin 13 y ⁇ on its side facing away from the closing head 14 projects in all three embodiments in the spring chamber 18, but is not performed in a separately provided in the first valve housing part 2 blind bore. A loading of the end face 32 of the valve pin 13 ⁇ ⁇ with a hydraulic force is therefore always in all embodiments with the pressure prevailing in the spring chamber 18 pressure.
  • the size of effectively acted upon by the pressure of the second pressure area end face 32 of the valve pin 13 ⁇ ⁇ be set regardless of the diameter of the second sealing seat ,
  • the diameter of the second sealing seat 12 and the diameter d 2 of the second guide portion 21 are identical.
  • the pressure in prevails the second pressure range and acts in the region 27 on the valve piston in the axial direction, then leads to no axial force on the valve piston 13 ⁇ ⁇ .
  • the diameter of the second sealing seat can also be greater than the diameter d 2 of the second guide portion 21.
  • the diameter of the spring plate 15 is further selected so that the formed on both sides of the spring plate 15 partial volumes of the spring chamber 18 via a gap on the outer circumference of the spring plate 15 are in fluid communication with each other.
  • the connecting channel 25 in the valve closing body 7 ⁇ is arranged obliquely to the valve longitudinal axis in the illustrated embodiment of FIG. 2 and connects an outer circumference of the valve closing body 7 ⁇ with the annular channel 26.
  • the region of the second guide portion 21 extending in the axial direction connecting channel be educated.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Safety Valves (AREA)
  • Details Of Valves (AREA)

Abstract

L'invention concerne un ensemble soupape de limitation de pression et soupape anticavitation. L'ensemble soupape de limitation de pression et soupape anticavitation sépare une première d'une deuxième zone de pression (5; 6, 20, 27) à l'aide d'un premier siège étanche et à l'aide d'un deuxième siège étanche. Pour former un premier siège étanche, une surface de fermeture de soupape (8) d'un corps de fermeture de soupape (7) coopère avec un siège de soupape (9). Pour former un deuxième siège étanche, une surface de siège de soupape (12) formée dans le corps de fermeture de soupape (7) coopère avec une tête de fermeture (14) disposé sur une tige de soupape (13). La tige de soupape (13) est précontrainte, au moyen d'un premier ressort de fermeture qui est tendu entre une coupelle de ressort (15) fixée à la tige de soupape (13) et le corps de fermeture de soupape (7), contre ce deuxième siège de soupape (12). Un module de soupape (7, 10, 13, 15, 17) comprenant le corps de fermeture de soupape (7), la tige de soupape (13), le premier ressort de fermeture (10) et la coupelle de ressort (15) est précontraint, au moyen d'un deuxième ressort de fermeture (35), contre le premier siège de soupape (9). La tige de soupape (13) est guidée de manière étanche dans au moins une première section de guidage (19) réalisée dans le corps de fermeture de soupape (7). Le deuxième siège de soupape (12) et la première section de guidage (19) sont disposés sur des côtés différents de la deuxième zone de pression (6, 20, 27) par rapport au sens de mouvement de la tige de soupape (13). La première section de guidage (19) sépare un volume (18) relié à la première zone de pression (5) de la deuxième zone de pression (6, 20, 27) ou un volume relié à la deuxième zone de pression. Une aire de la section transversale de la première section de guidage (19) est, à des fins de fixation d'une surface de la tige de soupape (13) soumise à la pression de la deuxième zone de pression, plus petite qu'une surface de section transversale du deuxième siège de soupape (12).
PCT/EP2009/007189 2008-10-08 2009-10-07 Ensemble soupape de limitation de pression et soupape anticavitation WO2010040511A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN2009801396499A CN102177375B (zh) 2008-10-08 2009-10-07 限压和抽吸阀单元
US13/122,473 US20110240897A1 (en) 2008-10-08 2009-10-07 Pressure Limiting And Suction Valve Unit

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008050864 2008-10-08
DE102008050864.0 2008-10-08

Publications (1)

Publication Number Publication Date
WO2010040511A1 true WO2010040511A1 (fr) 2010-04-15

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US (1) US20110240897A1 (fr)
CN (1) CN102177375B (fr)
DE (2) DE102009048438B4 (fr)
WO (1) WO2010040511A1 (fr)

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EP2405165B1 (fr) * 2010-07-07 2015-08-05 Aisin Seiki Kabushiki Kaisha Soupape de décharge
FR3033529B1 (fr) 2015-03-13 2018-05-18 Poclain Hydraulics Industrie Dispositif d'assistance hydraulique sur vehicule et procede de mise a vide d'un tel dispositif
FR3037375B1 (fr) * 2015-06-10 2017-06-02 Poclain Hydraulics Ind Dispositif de limitation de pression, notamment pour systeme d'assistance hydraulique de vehicules
EP3308057B1 (fr) * 2015-06-10 2020-08-05 Poclain Hydraulics Industrie Dispositif de limitation de pression, notamment pour système d'assistance hydraulique de véhicules
WO2016198655A1 (fr) * 2015-06-10 2016-12-15 Poclain Hydraulics Industrie Dispositif de limitation de pression, notamment pour système d'assistance hydraulique de véhicules
FR3039620B1 (fr) * 2015-07-28 2017-08-25 Poclain Hydraulics Ind Dispositif de limitation de pression notamment pour un systeme d'assistance de vehicule
US10539130B2 (en) * 2016-04-26 2020-01-21 Robert Bosch Gmbh Pressure-maintaining valve arrangement for a purge circuit of a closed hydraulic circuit
US11780275B2 (en) * 2020-09-02 2023-10-10 Deere & Company Valve fitting for a tire assembly of a working vehicle equipped with a central tire inflation system (CTIS)

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GB2064069A (en) * 1979-11-14 1981-06-10 Bosch Gmbh Robert A Check Valve Operating as a Pressure Limiting Valve and a Make-up Valve
DE3145118A1 (de) * 1981-11-13 1983-05-26 Robert Bosch Gmbh, 7000 Stuttgart Hydraulisches druckbegrenzungs- und nachsaugventil
DE102004026683A1 (de) * 2004-05-28 2005-12-15 Linde Ag Hydraulische Ventileinrichtung
DE102004061862A1 (de) * 2004-12-22 2006-07-06 Brueninghaus Hydromatik Gmbh Druckbegrenzungsventil mit reduzierter Differenzfläche

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DE102009048439B4 (de) 2022-03-17
US20110240897A1 (en) 2011-10-06
DE102009048438A1 (de) 2010-04-15
CN102177375A (zh) 2011-09-07
DE102009048439A1 (de) 2010-04-15
CN102177375B (zh) 2013-07-31
DE102009048438B4 (de) 2019-06-19

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